Towel collator



H. W. REHR TOWEL COLLATOR Dec. 13, 1966 7 Sheets-Sheet 1 Filed Aug. 28, 1964 H. W. REHR TOWEL COLLATOR Dec. 13, l96

7 Sheets-Sheet 2 Filed Aug. 28, 1964 Dec. T13, WM H. w. REHR 3,2Q11A7'? TOWEL COLLATOR Filed Aug. 28, 1964 7 Sheets-Sheet 5 Dec. 13, 1966 H. w. REHR TOWEL COLLATOR Filed Aug. 28, 1964 7 Sheets-Sheet 4 H. W. REH R TOWEL COLLATOR Dec. 13, 1966 7 Sheets-Sheet 5 Filed Aug. 28, 1964 INVENTOR. HAWYM Paw? BY fiz g flfiUQA/f/ Dec. 13, 1966 H. w. REHR 3,291,477

TOWEL COLLATOR Filed Aug. 28, 1964 '7 Sheets-Sheet e I.\'\ ENTOR. Msww 41, Fm?

BY ya H. W. REHR TOWEL COLLATOR Dec. 13, 1966 'T Sheets-Sheet 7 Filed Aug. 28, 1964 r R? W mM 9 m m M m fi United States Patent 3,291,477 TOWEL COLLATOR Henry W. Rehr, Concord, Califl, assignor to Crown Zellerbach Corporation, San Francisco, Calif., a corporation of Nevada Filed Aug. 28, 1964, Ser. No. 392,805 17 Claims. (Cl. 270-39) This invention relates to collating apparatus and, more particularly, to a collator especially useful in collecting and separating into bundles of appropriate count interfolded materials such as paper towels.

In describing the collating apparatus, it Will be convenient to consider the same as used in the bundling of interfolded towels of the type frequently found in public washrooms in dispensers that permit the towels to be withdrawn therefrom sheet-by-sheet. As a result of the interfolding of the towels, withdrawal of one sheet is efiective to partially withdraw the next successive sheet so that it can be conveniently grasped for subsequent withdrawal. In making such towels, the paper webs from which they are formed are withdrawn from parent rolls and are fed to interfolder mechanism whereat the webs are severed into towel lengths, are interfolded one with another, and are continuously discharged from the interfolder mechanism in such severed and interfolded relation. Such interfolder mechanisms are old and well known in the art and, as respects the present invention, may be completely conventional.

The collating apparatus constituting thepresent invention is operative to receive the interfolded sheets of towel material which is continuously discharged from the interfolder mechanism, collect the same into bundles each comprising a predetermined number of towels, and then separate the bundles for packaging. The particular collating apparatus considered herein as an exemplification of the invention includes a plurality of conveyor elements each having a continuous spiral flight defining a plurality of turns therealong leading from the infeed end to the discharge end of the collection conveyor formed thereby. An elevator located adjacent the discharge end of such conveyor receives the discharge therefrom, and when a sulficient number of sheets are positioned thereon transports the same to a discharge conveyor. The apparatus further includes structure operative in timed relation with the conveyor elements and elevator for separating the sheets of materials into groups or bundles of appropriate count (i.e., a predetermined number of sheets), and for initiating the start of each subsequent bundle during the period that the elevator is transporting a prior bundle to the discharge conveyor.

The provision of improved apparatus of this type is a general object of this invention; and additional objects and advantages especially of a particular nature will become apparent as the specification develops.

An embodiment of the invention is illustrated in the accompanying drawings, in which:

FIGURE 1 is a side view in elevation of a towel-making machine which includes towel interfolding, collating, and banding sections;

FIGURE 2 is an enlarged, broken end view in elevation looking toward the right in FIGURE 1;

FIGURE 3 is a vertical sectional view taken generally along the line 33 of FIGURE 2;

FIGURE 4 is a horizontal sectional view taken along the line 4-4 of FIGURE 2;

FIGURE 5 is a broken side view in elevation taken generally along the line 5-5 of FIGURE 4;

FIGURE 6 is a broken vertical sectional view taken along the line 66 of FIGURE 2;

FIGURE 7 is a transverse sectional view taken along the line 7-7 of FIGURE 3;

3 ,291,477 Patented Dec. 13, 19%6 FIGURE 8 is a vertical sectional view taken along the line 8-8 of FIGURE 7;

FIGURE 9 is a broken vertical sectional view taken along the line 9 9 of FIGURE 7;

FIGURE 10 is an enlarged, vertical sectional view illustrating one condition of the collator during an operational cycle thereof; and

FIGURE 11 is an enlarged, vertical sectional view similar to that of FIGURE 10 but showing the collator dur ing another condition in such operational cycle.

The towel making machine shown in its entirety in FIGURE 1 includes a towel interfolder mechanism 15, a towel collating apparatus 16, a transfer conveyor 17, and a banding device 18. The interfolder mechanism 15 in the illustrated machine is completely conventional, and for this reason will not be described. In accordance with its conventionality, it continuously discharges paper webs which have been severed into towel lengths and interfolded one with another to form an interconnected sequence thereof, as shown particularly in FIGURES l0 and 11. The collating apparatus 16 will be considered in detail herein including the cooperative relation thereof with the transfer conveyor 17, although for the most part, such conveyor as respects the structural components and function thereof may be conventional. Similarly, the banding device 18 may be a standard piece of equipment as, for example, the bander disclosed in Lowe et al. patent, No. 3,030,750.

The towel-making machine shown in FIGURE 1 takes continuous paper webs withdrawn from supply rolls (not shown) severs such webs and interfolds the same, and discharges the interfolded sheets continuously to the collator apparatus 16. The collator collects the interfolded sheets and separates the same into bundles of appropriate count (e.g., 250 in a typical instance), and deposits such bundles onto the transfer conveyor 17. The transfer conveyor intermittently advances such bundles (denoted with the numeral 19 in FIGURE 1) into the banding device 18 which has a ram mechanism 20 that displaces each such bundle upwardly and into a carriage assembly which transports the same to a turret 21 having a plurality of stations (six in the specific illustration) respectively adapted to receive such bundles. The turret successively indexes the bundles toward a discharge station, whereat each banded bundle may be placed within a shipping carton for storage and transport.

The banding of each bundle in the bander 18 is accomplished as part of the described operation thereof;

and in this respect, the paper banding material is withdrawn from a parent roll 22, is extended across the path of movement traversed by each bundle in being displaced by the ram mechanism 20 upwardly from the transfer conveyor 17 and into the carriage assembly thereabove, and the material is severed into band lengths so that such movement of a bundle into engagement with a band is effective to wrap the band thereabout. An adhesive is applied to the band during transfer of a bundle about which it is wrapped toward the turret 21, and the turret then receives and confines each bundle and its wrapper until the adhesive has set at which time the bundle is discharged from the turret.

The collator apparatus 16 includes frame structure, generally indicated as 23, which comprises transversely spaced end walls 24 and 25. Iournalled for rotation in the frame structure 23 are a plurality of conveyor elements, each of which has a continuous spiral flight defining a plurality of turns leading from one end to the other thereof. In the specific structure shown, there are four such conveyor elements (FIGURE 4) designated with the numerals 26, 27, 28 and 29, and respectively supported upon vertically oriented shafts 30 through 33 journalled for rotation in suitable bearing members provided by respectively associated frame components 34 through 37. These frame components are bolted or otherwise fixedly secured to the associated side walls 24 and 25. The conveyor elements 26 through 29 together define a collection conveyor, and are oriented in spaced apart relation with the spiral flights thereof aligned so as to receive the discharge of the interfolder mechanism 15 at the infeed end of the collection conveyor and to advance such material toward the discharge end thereof.

As shown best in FIGURE 2, the spiral conveyor elements 26 and 27 (and in particular the shafts 30 and 31 thereof) are respectively equipped adjacent their lower ends with bevel gears 38 and 39 which meshingly engage with a pair of bevel gears 40 and 41 fixedly mounted upon a drive shaft 43 extending between the frame elements 24 and 25 and journalled for rotation therein. The gears 40 and 41 are spaced apart along the shaft 43 which is supported therebetween by a hearing 42. At one end, the drive shaft 43 extends outwardly beyond the frame element 25 and is equipped thereat with a drive gear 44. The gear 44 is drivingly engaged by an idler gear 45 driven from the interfolder mechanism 15, as indicated in FIGURE 1.

In a similar manner, the spiral elements 28 and 29 and the shafts thereof are provided with bevel gears that mesh with complementary gears carried by a drive shaft equipped at its end with a gear driven by the idler 45; and in this respect, FIGURE 3 illustrates the spiral conveyor element 29 and shaft 33 thereof having a bevel gear 46 interengaging a gear 47 carried by a drive shaft 48 which, as shown in FIGURE 1, is provided with a gear 49 driven by the idler gear 45. Thus, the spiral conveyor elements 26 through 29 are driven in positive synchronism with each other and in synchronism with the interfolder mechanism 15.

The discharge of towels from the collection conveyor defined by the spiral conveyor elements 26 through 29 is ultimately received upon an elevator generally indicated with the numeral 50 (FIGURES 1 and 3) and which, as shown most clearly in FIGURES 2 and 4, includes a pair of transversely spaced elevator platforms 51a and 51b. The platforms 51a and 51b are generally rectangular, and at the outer ends thereof are fixedly secured to and thereby supported on guide blocks 52a and 52b that are slidably mounted upon rods 53a and 53b respectively associated therewith. The rods 53 are vertically oriented and at the lower ends thereof are fixedly secured to the adjacent frame walls 24 and 25, and at their upper ends they are respectively secured to straps 54a and 54bthe first of which is secured to the frame members 35 and 37, and the second of which is secured to the frame members 34 and 36. Thus, the rods 53 are fixedly located and the platforms 51a and 51b are axially displaceable therealong.

Such displacements of the elevator platforms are effected by means of connecting rods 55a and 55b pivotally connected at their upper ends to the respectively associated slide blocks 52a and 52b, each of which is provided with a recess along the underside thereof accommodating such pivotal connection. At their lower ends, the connecting rods 55a and 55b are pivotally connected, respectively, to crank arms 56a and 56b which, as shown best in FIGURE 3, have offset bifurcated end portions receiving the ends of such rods therein. The crank arms 56 extend forwardly and are fixedly secured to a transversely extending shaft 57 so that relative angular movement therebetween is prevented. The shaft 57 has fixed thereto one end of a drive arm 58 which, at the opposite end thereof, is equipped with a cam follower 59 that rides along the surface of a cam 60 constrained upon a shaft 61 so as to be rotatably driven thereby. The shaft 61, as shown most clearly in FIGURE 7, is equipped intermediate the ends thereof with a sprocket 62 having a link chain 63 entrained thereabout that is also entrained about a drive sprocket 64 providing the output of a gear reducer 65, the input of which originates in a motor 66.

Evidently then, whenever the motor 66 is energized, the drive sprocket 64 is rotated as is the sprocket 62 (through the chain 63). correspondingly, the shaft 61 is rotatably driven which, in turn, drives the cam 60. Since the cam follower 59 rides upon and follows the contour of the cam 60, and because it is connected to the arm 58 which in turn is connected to the shaft 57, the shaft is cyclically reciprocated angularly to the extent and at the rate determined by the cam configuration. Accordingly, the arms 56 are angularly reciprocated about an axis defined by the shaft 57; and because of the pivotal connection of the arms 56 to the elevator platforms 51 by means of the rods 55, the elevator is cyclically reciprocated toward and away from the discharge end of the collector conveyor defined by the spiral conveyor elements 26 through 29. As shown in FIGURES 7 and 9, the shaft 57 is resiliently biased in a clockwise direction (FIGURE 9) by a helical spring 67 which at one end (not shown) is connected to the frame structure, and at its upper end is connected to an arm 68 clamped to the shaft 57. Thus, the cam follower 59 is continuously urged into engagement with the contoured surface of the cam 60, and the spring effectively returns the elevator to its uppermost position after it has been displaced downwardly by the cam.

As shown in FIGURES 2, 7 and 8, the shaft 61 extends transversely of the transfer conveyor 17, and rotatably mounted upon the shaft is a drive sprocket 69. Bolted or otherwise fixedly secured to the drive sprocket 69 so as to rotate therewith is a clutch element 70 having a pair of drive teeth or notches 71 and 72 angularly spaced from each other by approximately 180. The clutch element 70 is disposed along the inner face of the cam 60, and carried by the cam along such inner face is a dog 73 supported for pivotal movement by a pivot pin 74 extending outwardly from the cam substantially normal to the plane of such inner face. The dog 73 is resiliently biased in a counter-clockwise direction (FIGURE 8) by a helical spring 75 secured at one end to a pin provided by the dog 73 and at its other end to a pin provided by the cam 60. Usually, a stop will be included to define the maximum permissible displacement of the dog 73 in the counterclockwise direction.

Evidently, as the cam 60 is rotated in a counter-clockwise direction (as viewed in FIGURE 8) by the shaft 61. the dog 73 at the leading end 76 thereof will be brought into abutment with the drive notch 71, whereupon continued rotational movement of the cam will cause the clutch element 70 to rotate concurrently therewith in the same counter-clockwise direction. Such concurrent rotation of the cam 60 and clutch element 70 will continue until the outer end portion 77 of the dog 73 is brought into engagement with a stationary stud 78 carried by a channel member 79 forming a part of the transfer conveyor 17. Thereafter, continued rotation of the cam 60 will cause the dog 73 to rotate about the pivot pin 74 thereof until the end 76 becomes disengaged from the notch 71 of the clutch element 70. At the time of this disengagement, the clutch element 70 will have advanced 180 from the position thereof shown in FIGURE 8; in which event the clutch element will have the same configuration as that illustrated except that the notches 71 and 72 will be exactly interchanged. As soon as the dog 73 has been rotated clear of the stud 76 and of the clutch element 70 by continued rotation of the cam 60, the dog will be returned to the position shown by the biasing force of the spring 75. Thus, for each 360 rotation of the drive shaft 61 and cam 60, the sprocket 69 will traverse a half-rotation or 180.

The drive sprocket 69 (as shown most clearly in FIG- URE 1) has an endless drive chain entrained thereabout which dn'vingly engages a sprocket 81 keyed to a shaft 82 so as to drive the same. Mounted upon the shaft 82 are a pair of transversely spaced drive gearsthe gear 83 being shown in FIGURE 1 in engagement with a gear 84 mounted upon a shaft 85 equipped with a pair of drive sprockets, one of which is shown in FIG- URE 1 and is denoted 86. The sprocket 86 has an endless chain entrained thereabout (FIGURE 3) which at its opposite end is entrained about a sprocket 87. The sprocket 87, as well as the corresponding sprocket which is identified as 88, are both shown in FIGURE 2, and are seen to be mounted upon separate shafts (respectively denoted 89 and 90) that are respectively supported by the aforementioned channel 79 and by its corresponding channel member 91 which is parallel therewith and extends along the opposite side of the conveyor 17.

The transfer conveyor 17 and, in particular, the endless chains provided thereby are equipped with a plurality of pushers oriented in transversely spaced pairs, each pair of which is generally designated in FIGURES 1 and 3 with the numeral 92. The pushers 92 are adapted to engage the rear edges of the successive groups or stacks 19 of towels and push the same forwardly (that is, from left to right as viewed in FIGURES 1 and 3) along the transfer conveyor and, in particular, along the stationary platform 93 thereof. As shown in FIGURE 2, such platform 93 comprises two transversely spaced and longitudinally extending platform sections 94a and 94b, and the pushers extend upwardly through the space defined therebetween. FIGURE 2 also illustrates that there are two such pushers in each pair '92, and for identification the two pushers in each pair are denoted 95a and 95b.

As shown in FIGURE 3 with respect to the pusher element 95a, each such pusher element is supported by a link or arm 96 pivotally carried by the associated chain 97 for angular displacements about a pivot pin 98. The pivot pin 98 secures the arm 96 intermediate the ends thereof to the chain 97, and the pusher 95a is fixedly anchored to the link 96 adjacent one end thereof. The opposite end of the link is provided with a cam follower 99 which is adapted to engage a stationary cam 100 as the pushers traverse the arc of curvature adjacent the infeed end of the conveyor to commence their advance toward the discharge end thereof Such cam 100 in association with the cam follower 99 is effective to raise each pusher to a generally normal disposition with respect to the chain 97, as shown in FIGURE 3, so that the pusher can engage the rear surface of a stack of towels 19 to push the same off of the elevator 50 and forwardly therefrom along the platform 93.

Cooperative with the conveyor 50 in forming the interfolded towels into bundles or stacks, and which in particular determines the count or number of towels in each such stack, is a separator mechanism generally denoted with the numeral 101. The separator mechanism 101 includes a plate 102 that is relatively thin and substantially flat, and is fixedly carried at one end of an arcuate arm 103 which at its other end is carried by a support link 104. In the particular structure shown, the end of the arcuate arm 103 associated with the link 104 is turned downwardly and extends through a collar 105 provided by such support link, and a plurality of set screws 106 threadedly extending into the collar 105 permit the precise angular position of the arm 103 to be selectively adjusted relative to the collar 105 and, therefore, relative to the support link 104.

The support link 104 adjacent the opposite end thereof is equipped with a sleeve 107 that coaxially receives a support rod 108 therein and is freely slidable axially therealong. The support rod 108 is vertically oriented and is secured at the supper end thereof to a link 109 and at its lower end to a link 110, each of which is clamped adjacent the inner end portion thereof to a drive shaft 111 that is vertically oriented and is substantially parallel to the support rod 108. The shaft 111 is journalled for ro- 8 tation adjacent opposite ends thereof in bearing structures 112 and 113 which are secured to and supported by the end wall 25 of the apparatus.

Adjacent its lower end portion, the shaft 111 has a drive link 114 fixedly secured thereto. The drive link 114 is pivotally connected to a push rod 115, which at its opposite end is pivotally connected to one arm 116 of a bell crank structure having the other arm 117 thereof supported for angular displacements about a pivot pin 118 fixedly located with respect to the frame structure of the apparatus. Such arm 117 of the bell crank structure is elongated and extends beyond the arm 116 so as to form a generally T-shaped configuration therewith, and it is provided with a cam follower 119 that engages the surface of a cam 120. A helical spring 121, secured at one end to the frame structure and at its other end to the arm 116 of the bell crank, biases such crank in a counterclockwise direction (as viewed in FIGURE 2) about the pivot pin 118 to continuously urge the cam follower 119 into engagement with the configurated surface of the cam 120.

The cam 120 (as shown most clearly in FIGURE 3) is mounted upon a shaft 122 so as to rotate therewith, and it is a two-piece cam comprising a cam element 123 that governs outward movement of the plate 102 in a direction away from the conveyor elements 26 through 29, as will be described in detail hereinafter; and a cam element 124 that governs the inward movement of the plate 102 towardsuch conveyor elements. The shaft 122 is appropriately journalled for rotation in bearing structure supported by the frame of the apparatus, and it is equipped at one end with a drive gear 125. The gear 125 is engaged by an idler gear 126 in meshing engagement with the output gear 127 of a gear box 128the input of which is provided by a sheave or pulley wheel 129 driven by an endless belt 130 which is driven by a sheave or pulley wheel 131 mounted upon the aforementioned drive shaft 43 driven from the interfolder mechanism through the gears 44 and 45. The usual take-up roller 132 engages the belt 130 to obviate slack therein.

The gear 125 provides a means for changing the count or number of towels in each stack 19 thereof since the rate of rotation of the cam 120 will vary in accordance with the diameter of such gear 125. Accordingly, the idler gear 126 is supported by a bracket or link 133 angularly displaceable relative to the axis of a pivot pin or shaft 134 that provides a mounting therefor. The link is provided with an elongated slot 135 therealong having a post or axle extending therethrough upon which the idler gear 126 is mounted. Evidently then, the axle of the idler gear 126 can be selectively located within the dimensional limits of the slot 135 to establish a meshing engagement of such idler gear with the gears 125 and 127. It may be noted that such axle of the gear 126 also extends through a mounting link 136 which is concentric with the axle of the drive gear 127, and which is angularly displaceable relative thereto. The two links 133 and 136 cooperate to fixedly support idler gears 126 in proper positions of adjustment therefor, and accommodate gears 125 of various diameters.

Evidently, then, not only are the spiral conveyor elements 26 through 29 driven in synchronism with each other and in enforced synchronism with the interfolder mechanism 15, but the separator mechanism (and particularly the plate 102 thereof) is repetitively and cyclically reciprocated in clockwise and counter-clockwise directions (as viewed in FIGURE 4) between the two (inner and outer) positions indicated therein in enforced synchronism with such interfolder mechanism because of the drive defined from the shaft 43 through the sheave 131, endless belt 130, sheave 129, gear box 128, gears 127, 126 and 125, shaft 122, cam 120, cam follower 119 and bell crank defined by the arms 117 and 116, push rod 115, and drive link 114.

The drive link 114 in being secured to the shaft 111 angularly reciprocates the same about the longitudinal axis thereof in accordance with the configurations defined by the two cam elements 123 and 124 which together form the in-out or angular-motion cam 120. In accordance with the angular displacements of the shaft 111, the support links 109 and 110 together with the shaft 108 are rotated relative to the longitudinal axis of the shaft 111; and, therefore, the plate 102 is reciprocated between the inner and outer positions thereof because of its connection to the shaft 108 through the link 104 and arcuate arm 103. It may be noted that the sleeve 107 that interrelates the link 104 and shaft 108 is axially slidable along such shaft, and in the structure illustrated may be angularly displaceable with respect thereto. However, the sleeve is constrained against any such angular displacements in that it is connected by a strap 137 with a sleeve 138 which is mounted upon the shaft 111 and is freely slidable therealong. In actual practice, the shaft 111 may be square-shaped or otherwise polygonal in cross section (in which event the passage through the sleeve 138 will have a complementary configuration) so as to directly impart angular movement to the sleeve 138 whenever the shaft 111 is pivoted through the linkage defined by the elements 114, 115, 116-117, cam follower 119 and the cam 125.

As well as being cyclically displaceable between the inner and outer positions illustrated in FIGURE 4, the separator mechanism 101 (and in particular the plate 102 thereof) is vertically displaceable between an upper position generally aligned with the upper ends of the spiral conveyor elements 26 through 29 (as indicated in FIG- URE 2) and a lowermost position below such conveyor elements, as indicated in FIGURE 6such positions of the plate 102 are indicated more clearly in FIGURES and 11, and will be considered in somewhat greater detail in describing an operational cycle of the apparatus. Vertical movement is imparted to the plate 102 through the arm 103, support 104 and sleeve structures 107 and 138 which are interconnected by a rigid strip 137 and are slidably supported, respectively, upon the shafts 108 and 111.

As seen in FIGURES 2 and 5, a push rod 139, which may have an adjustable head 140 to facilitate selective determination of the length thereof, is pivotally secured at its upper end to the sleeve 138 and at its lower end is connected to a lever arm 141 through a swivel connection 142 which, for example, may be a ball and socket connector. The lever 141 extends toward the frame wall 24 and is pivotally supported thereat by a rod 143 which is journalled in bearings 144 and 145 (see FIGURE 3) supported by the frame wall 24. Intermediate its ends, the lever 141 is equipped with a cam follower 146 that rides upon a cam 147 which is mounted upon the aforementioned shaft 122 so as to rotate therewith. Consequently, the up-down or vertical-motion cam 147 rotates concurrently with the cam 120; and, therefore, both are driven in synchronism with the interfolder mechanism and with the spiral conveyor elements 26 through 29 by means of the aforementioned gear train including, in part, the endless belt 130, and gears 127, 126 and 125.

As a result of this arrangement, it is evident that the separator mechanism 101, and in particular the plate 102 thereof, is cyclically reciprocable in vertical directions to an extent determined by the configuration of the cam 147 which thereby causes angular displacements of the lever 141 and, through the rod 139 that is secured thereto and through the sleeve 138, corresponding vertical movement of the support 104 and arm 103 to reciprocate along the vertical axis defined by the shaft 111. Not only is the extent or length of the reciprocable displacement determined by the cam 147, but the rates of upward and downward displacements are also determined thereby and, it may be noted, such displacements are not necessarily at the same velocities. Actually, the rate of downward displacement of the mechanism 101 is made equal to the lead of the spiral flights defined by the conveyor elements 26 through 29, and is carefully controlled so that the plate 102 is not drivingly engaged by such conveyor elements in moving downwardly therethrough, as will be described hereinafter.

Also operative in effecting separation of one bundle from another is an auxiliary separator or clamp structure generally denoted 148 (FIGURES 2, 3 and 6). The clamp structure 148 includes a pair of separator or clamp fingers 149a and 149!) that are carried on a cross member 150 carried by a post 151 adjustably connected to a post extension or support 152. The support and post are fastened together by a pin or cap screw that extends through an elongated slot 153 in the support 152 and thereby permits adjustable positioning of the post 151 relative thereto within the dimensional limits of the slot.

At its lower end, the support 152 is fixedly secured by cap screws or other suitable means to a link 154 supported for pivotal movement on a pin 155 provided by a bracket 156 that is bolted or otherwise fixedly secured to frame elements proximate thereto. Intermediate its ends, the support 152 is provided with a laterally extending cam follower 157 that rides along the cam-configurated surface of a cam element 158 mounted upon the aforementioned shaft 89 so as to rotate therewith. Consequently, the cam 158 is intermittently rotated and is angularly displaced through approximately 180 relative to the axis of the shaft 89 whenever the transfer conveyor 17 is intermittently energized, as described hereinabove.

The cam follower 157 is resiliently biased into engagement with the cam 158 by a helical spring 159 which at its lower end is secured to an car 160 provided by the link 154, and at its opposite end the spring is secured to "a platform element 161. During each 180 displacement of the cam 158, the clamp structure 148 is displaced inwardly from the normal outermost position thereof illustrated in full lines in FIGURE 6 into the innermost position thereof shown by broken lines in such figure, and is then returned outwardly to such outermost position. The function of the clamp structure, and in particular the fingers 149a and 14% thereof, during such angular displacement is to effect a positive separation between the uppermost towel in a stack 19 being lowered by the elevator 50 and the lowermost towel in the next successive stack being supported upon the separator plate 102-which two towels were, prior to separation, interfolded and therefore interconnected.

Following separation of such two towls respectively defining the last towel of a prior stack and the first towel of the next successive stack, such first towel depends downwardly and might not seat properly upon the elevator 50 when it ascends to pick up such next successive stack. In order to assure proper seating of the tail, a tail kicker or tail lifting mechanism (generally denoted 162) is incorporated in the apparatus. As shown most clearly in FIGURES 2 and 3, the tail kicker includes a U-shaped element comprising a paid of legs 163a and 16% integrally interconnected at their lower ends by a base 164 extending therebetween. The U-shaped member is arcuate in side view with the leg end portions adjacent the base 164 being substantially horizontally disposed.

The opposite ends of the legs are clamped to a shaft 165 journalled for rotation in bearing elements 166 and 167 suitably supported by the frame structure. The shaft 165 projects beyond the bearing structure 167, and is equipped thereat with a link 168 having pivotally secured thereto the adjustable upper end portion 169 of a push rod 170 which is threadedly connected to such upper end portion to permit adjustment of the effective length of the rod. At its lower end, the rod 170 is similarly connected pivotally to a triangularly-shaped crank arm 171 adjacent one corner portion thereof. The crank arm is pivotally supported adjacent another corner thereof on a pin 172; and adjacent its remaining corner, the crank arm is pivotally connected to a drive rod 173 on one end 9 thereof which, at its opposite end, is pivotally connected to one arm 174 of a bell crank.

The other arm 175 of the bell crank is provided with a laterally extending cam follower 176 (FIGURE 7) that rides upon the surface of a cam 177 clamped to the aforementioned shaft 61 which is intermittently driven by the motor 66 and thereby energizes the reciprocatory displacements of the elevator 50. Thus, the tail lifter or kicker assembly 162 is energized in timed relation with the reciprocatory displacements of the elevator 50; and for each complete rotation of the shaft 61, the cam 177 is rotated through 360. As a result thereof, the cam follower 176 reciprocates the bell crank which, in turn, reciprocates the rod 173, thereby angularly displacing the triangularly-shaped crank 171 around the pivot pin 172 therefor. By this motion of the crank, the push rod 170 is reciprocated, the link 168 is angularly displaced about the axis of the shaft 165, and the U-shaped fingers 163a and 16311 are reciprocated between the outermost position thereof shown in FIGURE 3 and an inner position indicated in FIGURE 11. The cam follower 176 is biased into engagement with the cam by a helical spring 178 that at one end is connected to a pin provided by the crank 171, and which at its opposite end is connected to an eyelet or bracket element 179 secured to the channel member 91.

Rotational movement is enforced on the spiral conveyor elements 26 through 29 because of their driving connection via the gears 44 and 45 with the interfolder mechanism 15; and for this same reason, the cyclically repetitive motion of the separator mechanism 101 is determined by the interfolder mechanism. Energization of the elevator 50, transfer conveyor 17, auxiliary separator mechanism 148, and tail-lifting mechanism 142, however, is not directly determined by the interfolder mechanism 15 because a separate motor drive is provided which controls these components. Nevertheless, the operation thereof must be timed with that of the separator mechanism 101; and in the particular apparatus being considered, such timing is accomplished through circuitry including a microswitch 180 (FIGURES 2 and 3) adapted to be tripped or actuated by an actuator arm 181 clamped to the shaft 122 so as to rotate therewith. It will be recalled that the shaft 122 is rotated continuously because it is driven from the interfolder mechanism 15 through the drive train that includes, in part, the gears 125, 126 and 127 and the endless belt 130 which is driven by the gear 44 through the shaft 43 and sheave 131.

The microswitch 180 is used to initiate operation of the drive train originating with the motor 66; and evidently then, such drive is energized once during each 360 rotation of the shaft 122 because the actuating arm 181, in being constrained upon the shaft, traverses the same angular distance. Thus, the elevator 50 will commence its cycle of operation at proper intervals with respect to the movement of the separator mechanism 101 because the movement thereof is controlled by the cams 120 and 147 which cams are mounted upon the shaft 122 and rotate in a one-to-one time relationship therewith.

Also included in the apparatus is a second microswitch 182 (FIGURE 7) which is adapted to be actuated by a lever arm 183 clamped to the shaft 61 so as to rotate therewith. The shaft 61 is rotated whenever the motor 66 is energized because of the driving connection defined therebetween by the endless chain 63 and associated components, as shown in FIGURE 3. Thus, for each complete 360 rotation of the shaft 61, the actuator arm 183 trips the microswitch 182, and it is connected in a circuit arrangement such that it terminates operation of the gear train starting from the motor 66 whenever the switch is tripped. Therefore, the microswitch 180 is essentially a counter device which initiates operation of the elevator 50 whenever a bundle comprising a predetermined number of towels is supported thereon.

In this respect, the rate of delivery of interfolded towels from the interfolder mechanism 15 is a known quantity, as is the angular velocity of the spiral conveyor elements 26 through 29. Therefore, each time such conveyor elements make a predetermined number of revolutions, a determinate number of towels will be advanced therethrough. Clearly then, since the rotational movement of the shaft 122 is directly tied to the angular rotation of the conveyor elements 26 through 29, the number of rotations of the conveyor elements for each single rotation of the shaft 122 is readily determined. It may be said then that the switch is responsive to the number of towels delivered by the conveyor elements 26 through 29 to the elevator 50 to initiate operation of the elevator.

In a similar manner, the switch 182 is, in effect, sensitive to the position of the elevator and is responsive to a particular position thereof to terminate its cycle of operation. More particularly, whenever the drive from the motor 66 is completed because of the microswitch 180 being actuated, the shaft 61 will make one complete rotation as will the cam 60 which is mounted thereon. As a result, the elevator 50 will be displaced downwardly from the uppermost position thereof to its lowermost position of substantial alignment with the transfer conveyor 17, and will then be returned upwardly to its starting position. At about the instant that the elevator has returned to its uppermost position, the actuating arm 183 will trip the microswitch 182 which is effective to demergize the elevator drive from the motor 66.

Various arrangements may be employed in association with the cycle-starting or -initiating microswitch 180 and the cycle-stopping or -terminating microswitch 182; and it may be noted that there are a number of conventional arrangements which are quite suitable. For this reason, a schematic diagram of a control circuit has been omitted as unnecessary. By way of example, the two switches could be arranged in circuit with a self-holding relay such that when the switch 180 is tripped, the relay is energized to complete the circuit through the motor 66. Such self-holding relay then maintains itself in the energized state until the switch 182 is subsequently tripped, which is effective to momentarily break the self-holding circuit for the relay and thereby deenergizes the same. Another arrangement that can be used includes a type of one-revolution clutchin which event the motor 66 is continuously energized. However, it is only drivingly connected to the gear 64 by actuation of the switch 180. Thereafter, the clutch terminates the driving connection between the motor and gear whenever the switch 182 is actuated. An arrangement of this general type is illustrated and described in greater detail in my copending patent application, Serial No. 310,794, filed September 23, 1963.

Operation In describing a cycle of operation of the collating apparatus, reference will be made in particular to FIG- URES 10 and 11. Referring thereto, it is seen that a plurality of interfolded towels 184 and 185 are fed downwardly in a continuous stream from the interfolder mechanism 15 (FIGURE 1) to the collection conveyor comprising the spiral conveyor elements 2.6 through 29. All of these conveyor elements are disposed with the spiral flights thereof in alignment, and the interfolded towels enter such flights and are advanced downwardly therethrough toward the lower discharge end of the conveyor elements. It will be assumed initially that the components have the relative positions illustrated in FIGURE 10; in which event the interfolded towels discharged by the spiral conveyor elements are directed onto the elevator 50 which is in the uppermost position thereof.

Accordingly, the clamp structure or auxiliary separator structure 148 and the tail-lifting structure 162 are both in the open positions thereof; and if the separator mechanism 101 (and in particular the plate 102 thereof) is in the uppermost position illustrated, the number of interfolded towels supported between the elevator 50 and the upper entrance ends of the spiral conveyor elements is approaching the maximum number of towels to complete a bundle 19 thereof. Although the bundles 19 may comprise any suitable number of towels, it may be stated by way of example that bunldes of 150 and of 250 towels are common in the industry.

Since the bundle is nearing completion, the separator plate 102 moves inwardly and downwardly through the spiral flights defined by the forward conveyor elements 28 and 29 (FIGURE 4) toward the innermost position thereof shown in FIGURES 4 and 11. As a specific example, if the stack 19 is to comprise 250 towels, the inward movement of the plate 102 is so timed that at the instant it enters the gap between two successive towels, such towels define the 250th towel in one stack and the first towel in the next successive stack. Various positions of the plate 102 in so separating such towels is illustrated by broken dash lines in FIGURE 10.

It should be noted that the path of travel traversed by the separator plate 102 in moving from the upper outer position thereof shown by broken lines in FIGURE 4 into the lower inner position shown by full lines in such figure (also shown in FIGURE 11) is both inwardly and downwardly. More particularly, the plate 102 passes through the spiral flights defined by the two conveyor elements 28 and 29 in moving to such lowermost inner posi tion; and as stated hereinbefore, the velocity of the plate 102 during such movement thereof through the spiral flights is essentially equal to the lead thereof. Further, the motion of the separator plate is positively controlled to the extent that substantially no physical contact occurs between the plate 102 and the flights of the conveyor elements 28 and 29. For convenience, various successive positions of the separator plate 102 are illustrated in phantom in FIGURE 10.

As previously explained, the motion of the separator mechanism 101 is directly synchronized with the rotational movement of the conveyor elements 26 through 29, and, therefore, the inward and downward motion of the separator plate 102 through the spiral flights of the conveyor elements 28 and 29 occurs automatically as the final sheet of toweling completing a bundle or stack thereof comes into cooperative engagement with the conveyor elements adjacent the infeed ends thereof. Quite evidently, the plate 102 provides, at the time it has arrived at its innermost lower position, a divider between the sheets of toweling therebelow and those disposed thereabove.

The stack of towels located below the separator plate is supported upon the elevator 50 which commences its descent toward the transfer conveyor 17 in response to the triggering action of the microswitch 180 which is actuated by the arm 181 as a result of the rotational motion imparted thereto by the shaft 122. The shaft, it will be recalled, is continuously rotating because it is drivingly connected to the interfolder mechanism 15 through the endless belt 130 and drive members operatively associated therewith.

When the switch 180 is actuated, the energizing circuit of the motor 66 is completed and the elevator 50 is thereby displaced downwardly toward the transfer conveyor 17. For a brief interval, both the elevator 50 and separator plate 102 move downwardly together although the donwward motion of the separator plate is relatively slow with respect to that of the elevator. As a consequence, the two stacks or bundles respectively located above and below the plate 102 tend to separate one from the other in a vertical direction.

At about the time that the elevator is approaching the transfer conveyor 17, the auxiliary separator mechanism or clamp mechanism 148 is actuated and the inward movement thereof brings the fingers 149a and 1491; into engagement with the uppermost towel in the stack 19 then being moved into position on the transfer conveyor 17,

as illustrated in FIGURE 11. The fingers 149 press the uppermost towel downwardly against the stack and thereby frictionally constrain such towel against movement relative thereto. At the same time, the lowermost towel in the stack thereabove, which stack is being supported by the separator plate 102, is firmly held by the separator plate. Consequently, since the uppermost towel in the lower stack 19, which stack is being moved downwardly by the elevator 50, and the lowermost towel in the next successive stack thereabove, which next stack is being formed upon the separator plate 102, are being respectively gripped by the fingers 149 and by separator plate 102, and because the two stacks are moving away from each other, such two towels are positively separated without disturbing the other towels in either of the stacks.

The elevator 50, as shown in FIGURE 2, comprises two transversely spaced platforms 51a and 51b; and, therefore, the pusher elements 92 of the transfer conveyor 17 may pass freely therebetween. At about the time that the elevator 50 reaches its lowermost position so that the stack 19 along the lower surface thereof is in substantial alignment with the transfer conveyor, one pair of pusher elements thereof engage such stack and advance the same forwardly from ,the elevator 50. Following the short period of dwell of the elevator in its lowermost position which permits such displacement of the stack 19 therefrom, the elevator commences its ascent.

At about this time, the tail-lifting mechanism 162 is actuated whereupon the U-shaped legs 163a and 1625b thereof are cycled inwardly from the outermost position thereof shown in FIGURE 3 (also illustrated in full lines in FIGURES 10 and 11) into the innermost position thereof shown by broken lines in FIGURE 11. This inward movement of the U-shaped tail-lifter brings the same into engagement with the depending tail of the stack being formed on the separator plate 102, which tail is defined by the sheet 185 in the FIGURE 11 illustration. The lifter fingers carry the depending tail inwardly and upwardly and into a position in which it extends generally along the undersurface of the separator plate 102. Quite evidently then, the lifted tail 185 must also extend along the plane of the elevator platforms 51 when engaged thereby as the elevator moves upwardly. As seen in FIG- URE 2, the legs 163a and 163b of the tail-lifter are dimensioned so as to pass freely through the gap defined between the transversely spaced elevator platforms 51a and 51b and, then, the lifter mechanism does not interfere with the upward movement of the elevator. The fingers 163a and 163b are immediately returned to their outer position.

As the ascending elevator 50 moves into generally horizontal alignment with the separator plate 102, the elevator engages the stack of towels then being supported upon the separator plate and lifts such stack slightly therefrom. Again, the separator plate is dimensioned so as to pass through the space defined between the elevator platforms 51a and 51b, and once the stack has been displaced upwardly from the separator plate, it is free to swing outwardly and into the position shown by broken lines in FIGURE 4. The separator plate next moves upwardly and into a position generally above the elevation of the conveyor elements 26 through 29 to commence another cycle of operation.

The rate of downward movement of the separator plate 102 decreases at about the time it emerges from the discharge end of the spiral conveyor elements so as to force the collection of a group of interfolded sheets or towels thereabove. Thus, the downward motion of the separator plate 102 is not uniform and, in fact, the motion thereof is decreased to a lesser rate after the plate emerges from the continuous turns of the spiral flights of the conveyor elements 28 and 29,

It will be appreciated that the partciular number of towels in a stack is influenced by both the cam controlling the horizontal movements of the separator plate and the cam 147 controlling the verticcal motion thereof. Evidently, then, changing either of these cams will alter the cycle time of the separator and, correspondingly, the number of towels in a stack. However, irrespective of the particular cams employed, the concurrent inward and downward motions of the separator plate 102 are controlled so that the plate does not engage the spiral flights of the conveyor elements 28 and 29, and it may be said that these movements of the separator plate are essentially fixed for any given pitch of the spiral flights and rotational velocity of the conveyor elements.

The auxiliary separator 148 is operative in association with the conveyor 50 to maintain a stack 19 of towels in a vertical orientation as such stack is moved downwardly toward the transfer conveyor. The separator 148 further effects a positive separation between the towels in one stack and another. The tail-lifting mechanism 162 effectively assures that the first or lowermost towel in each stack is flat and smooth.

While in the foregoing specification an embodiment of the invention has been described in considerable detail for purposes of adequately disclosing the same, it will be apparent to those skilled in the art that numerous changes may be made in such details without departing from the spirit and principles of the invention.

I claim:

1. In combination with an interfolder in which sheets of material in interfolded relation are discharged therefrom, a plurality of rotatable conveyor elements together providing an axially extending collection conveyor operative to advance such interfolded sheets of material axially therethrough, each of said conveyor elements having a continuous spiral flight therealong leading axially from the infeed end to the discharge end of said collection conveyor, an elevator 'movable between the discharge end of said collection conveyor whereat it receives the discharge therefrom and a remote location for transferring thereto such discharge from said collection conveyor, a separator mechanism movable into said collection conveyor from a position laterally outwardly therefrom and also being axially movable therethrough so as to be insertable into the interfolded material discharged from said interfolder to divide the material into individual stacks of which the material disposed between said elevator and one side of said separator mechanism constitutes one such stack and the material collecting along the opposite side of said separator constitutes another stack, and drive mechanism including means for synchronously rotating said conveyor elements, also including means for reciprocating said elevator in timed relation therewith and further including means for cyclically moving said separator mechanism into and out of the path of such interfolded material and axially through said collection conveyor in timed relation with the rotational movement of said conveyor elements to effect such separation of the interf-olded material into stacks.

2. In combination with an interfolder in which sheets of material in interfolded relation are discharged therefrom, a plurality of rotatable conveyor elements together providing a collection conveyor operative to advance such interfolded sheets of material therethrough, each of said conveyor elements having a continuous spiral flight therealong leading from the infeed end to the discharge end of said collection conveyor, an elevator movable between the discharge end of said collection conveyor whereat it receives the discharge therefrom and a remote location for transferring thereto such discharge from said collection conveyor, a separator mechanism insertable into the spiral flight of at least one of said conveyor elements and being movable therethrough to divide the interfolded material being advanced by said collection conveyor into two individual stacks of which the material disposed between said elevator and one side of said separator mechanism constitutes one such stack and the material collected along the opposite side of said separator mechanism con- 14 stitutes another stack, and drive mechanism including means for synchronously rotating said conveyor elements, also including means for reciprocating said elevator in timed relation therewith and further including means for cyclically moving said separator mechanism into and out of the path of such interfolded material and through the flight of said one conveyor element in timed relation with the rotational movement of said conveyor elements to effect such separation of the interfolded material into stacks.

3. The combination of claim 2 and further including an auxiliary separator mechanism movable into engagement with the terminal sheet of a stack of material being displaced by said elevator in a direction away from said conveyor elements to facilitate separation of such terminal sheet from the next successive sheet discharged in interfolded relation therewith from said interfolder, and drive means connected with said auxiliary separator mechanism for actuating the same in timed relation with the movement of said elevator.

4. The combination of claim 2 and further comprising tail-lifting mechanism for displacing the initial sheet of a stack of material into general juxtaposition therewith so that such sheet will lie fiat along said elevator when the elevator is displaced into engagement therewith in moving toward said conveyor elements, and drive means connected with said tail-lifting mechanism for actuating the same in timed relation with the movement of said elevator.

5. In combination with an interfolder in which sheets of material in interfolded relation are discharged therefrom, a plurality of rotatable conveyor elements together providing a collection conveyor operative to advance such interfolded sheets of material therethrough, each of said conveyor elements having a continuous spiral flight therealong leading from the infeed end to the discharge end of said collection conveyor, an elevator movable between the discharge end of said collection conveyor whereat it receives the discharge therefrom and a remote location for transferring thereto such discharge from said collection conveyor, a separator mechanism insertable into the spiral flights of at least certain of said conveyor elements and being movable therethrough to divide the interfolded material being advanced by said collection conveyor into two individual stacks of which the material disposed between said elevator and one side of said separator mechanism constitutes one such stack and the material collected along the opposite side of said separator mechanism constitutes another stack, and drive mechanism including means for synchronously rotating said conveyor elements, also including means for reciprocating said elevator in timed relation therewith and further including means for cyclically moving said separator mechanism into the path of such interfolded material and through the spiral flights of said certain conveyor elements and for then maintaining the separator mechanism adjacent the discharge end of said collection conveyor while said elevator displaces a stack of material supported thereon to such location remote from the discharge of said collection conveyor and for thereafter returning said separator mechanism to its initial position.

6. The combination of claim 5 in which said last mentioned means for cyclically moving said separator mechanism comprises a positive interconnection therebetween so as to advance the same through the spiral flights of said certain conveyor elements without substantial physical engagement occurring therebetween.

7. The combination of claim 5 and further comprising an auxiliary separator mechanism movable into engagement with the terminal sheet of a stack of material being displaced by said elevator in a direction away from said conveyor elements to facilitate separation of such terminal sheet from the next successive sheet discharged in interfolded relation therewith from said interfolder, drive means connected with said auxiliary separator mechanism for actuating the same in timed relation with the movement of said elevator, tail-lifting mechanism for displacing the initial sheet of a stack of material into general juxtaposition therewith so that such sheet will lie flat along said elevator when the elevator is displaced into engagement therewith in moving toward said conveyor elements, and additional drive means connected with said tail-lifting mechanism for actuating the same in timed relation with the movement of said elevator.

8. The combination of claim and further comprising a transfer conveyor defining the aforementioned location remote from the discharge of said collection conveyor for receiving each stack of material displaced thereto by said elevator, and means comprised by said drive mechanism for energizing said transfer conveyor in timed relation with the movement of said elevator for removing each stack of material therefrom.

9. In a collator operative to separate sheets of material fed thereto into stacks each comprising a predetermined number of sheets, a plurality of rotatable conveyor elements together providing a collection conveyor for advancing such sheets of material theret'hrough and each conveyor element having a continuous spiral flight therealong defining a pluraity of turns leading from the infeed end to the discharge end of said collection conveyor, an elevator movable between the discharge end of said collection conveyor whereat it receives the discharge therefrom and a remote location for transferring thereto suchdischarge from said collection conveyor, a separator mechanism insertable into the spiral flights of at least certain of said conveyor elements and being cyclically movable therethrough to divide the material being advanced by said collection conveyor unto successive stacks of which in each instance the material disposed between said elevator and one side of said separator mechanism constitutes one such stack and the material collected along the opposite side of said separator mechanism constitutes another stack, and drive mechanism including means for synchronously rotating said conveyor elements, also including means for reciprocating said elevator in a time relationship therewith and further including means for cyclically moving said separator mechanism into and out of the path of such material in a time relationship with the rotation of said conveyor elements to effect such separation of the material into stacks.

10. In a collator operative to separate sheets of material fed thereto into stacks each comprising a predetermined number of sheets, a plurality of rotatable conveyor elements together providing a collection conveyor for advancing such sheets of material therethrough and each conveyor element having a continuous spiral flight therealong defining a plurality of turns leading from the infeed end to the discharge end of said collection conveyor, an elevator movable between the discharge end of said collection conveyor whereat it receives the discharge therefrom and a remote location for transferring thereto such discharge from said collection conveyor, a separator mechanism insertable into the spiral flights of at least certain of said conveyor elements and being cyclically movable therethrough to divide the material being advanced by said collection conveyor into successive stacks of which in each instance the material disposed between said elevator and one side of said separator mechanism constitutes one such stack and the material collected along the opposite side of said separator mechanism constitutes another stack, and drive mechanism including means for synchronously rotating said conveyor elements, also including means for reciprocating said elevator in a timed relationship therewith and further including means for cyclically moving said separator mechanism through the spiral flights of said certain conveyor elements and into the path of such material and for maintaining the separator mechanism adjacent the discharge end of said collection conveyor while said elevator displaces a stack of material supported thereon to such location remote from the discharge of said collection conveyor and for thereafter returning said separator mechanism to its initial position.

11. The collator of claim 10 in which the sheets of material fed thereto are interfolded, and further including an auxiliary separator mechanism movable into engagement with the terminal sheet of a stack of material being displaced by said elevator in a direction away from said conveyor elements to facilitate separation of such terminal sheet from the next successive sheet then supported by said first mentioned separator mechanism, and drive means connected with said auxiliary separator mechanism for actuating the same in timed relation with the movement of said elevator.

12. The collator of claim 10 in which the sheets of material fed thereto are interfolded, and further comprising tail-lifting mechanism for displacing the initial sheet of a stack of material into general juxtaposition therewith so that such sheet will lie flat along said elevator when the elevator is displaced into engagement therewith in moving toward said conveyor elements, and drive means connected with said tail-lifting mechanism for actuating the same in timed relation with the movement of said elevator.

13. The collator of claim 10 in which the sheets of material fed thereto are interfolded, and further comprising an auxiliary separator mechanism movable into engagement with the terminal sheet of a stack of material being displaced by said elevator in a direction away from said conveyor elements to facilitate separation of such terminal sheet from the next successive sheet then supported by said first-mentioned separator mechanism, drive means connected with said auxiliary separator mechanism for actuating the same in timed relation with the movement of said elevator, tail-lifting mechanism for displacing the initial sheet of a stack of material into general juxtaposition therewith so that such sheet will lie flat along said elevator when the elevator is displaced into engagement therewith in moving toward said conveyor elements, and additional drive means connected with said tail-lifting mechanism for actuating the same in timed relation with the movement of said elevator.

14. In a collator operative to separate sheets of material fed thereto into stacks each comprising a predetermined number of sheets, a plurality of rotatable conveyor elements together providing a collection conveyor for advancing such sheets of material therethrough and each conveyor element having a continuous spiral flight therealong defining aplurality of turns leading from the infeed end to the discharge end of said collection conveyor, a separator mechanism supported for linear and angular movements generally along the length of said conveyor elements and from a position laterally outwardly of said conveyor elements into and through the spiral flights of at least certain of said conveyor elements to a position in the path of the material being advanced by said collection conveyor to divide such material into successive stacks, and drive mechanism including means for synchronously rotating said conveyor elements and also including means for cyclically moving said separator mechanism into and through the spiral flights of said certain conveyor elements and for thereafter returning said separator mechanism to its initial position all in a time relationship with the rotational movement of said conveyor elements.

15. In a collator operative to separate sheets of material fed thereto into stacks each comprising a predetermined number of sheets, a plurality of rotatable conveyor elements together providing a collection conveyor for advancing such sheets of material therethrough and each conveyor element having a continuous spiral flight therealong defining a plurality of turns leading from the infeed end to the discharge end of said collection conveyor, a separator mechanism including a plate and a support structure therefor mounted for linear displacements generally along the lengths of said conveyor elements and also for transverse displacements from a position in which said plate is disposed laterally outwardly of said conveyor elements and is then moved into and through the spiral flights of at least certain of said conveyor elements to a position in the path of the material being advanced by said collection conveyor to divide such material into successive stacks, and drive mechanism including means for synchronously rotating said conveyor elements and also including means for cyclically displacing said support structure to move said plate into and through the spiral flights of said certain conveyor elements and for thereafter returning said plate to its initial position all in a time relationship with the rotational movement of said conveyor elements.

16. The collator of claim 15 in which said support structure comprises an arm mounted for angular displacements about an axis spaced from and substantially parallel to the axes of rotation of said conveyor elements to effect such transverse displacements of said plate, and

18 in which said arm is also reciprocable along such axis to effect the aforementioned linear displacements of said plate.

17. The collator of claim 16 in Which the aforesaid means for cyclically displacing said support structure includes a pair of cam members respectively controlling the angular displacements of said arm and the reciprocable movement thereof and includes also a pair of cam follower elements respectively associated with said cam members and with said arm, said cam members being rotatably driven with said conveyor elements to enforce the aforementioned time relationship therewith.

References Cited by the Examiner UNITED STATES PATENTS 1,886,312 11/1932 Stanton 27039 2,675,747 3/1954 Greiner et al. 9393 EUGENE R. CAPOZIO, Primary Examiner. 

1. IN COMBINATION WITH AN INTERFOLDER IN WHICH SHEETS OF MATERIAL IN INTERFOLDED RELATION ARE DISCHARGED THEREFROM, A PLURALITY OF ROTATABLE CONVEYOR ELEMENTS TOGETHER PROVIDING AN AXIALLY EXTENDING COLLECTION CONVEYOR OPERATIVE TO ADVANCE SUCH INTERFOLDED SHEETS OF MATERIAL AXIALLY THERETHROUGH, EACH OF SAID CONVEYOR ELEMENTS HAVING A CONTINUOUS SPIRAL FLIGHT THEREALONG LEADING AXIALLY FROM THE INFEED END TO THE DISCHARGE END OF SAID COLLECTION CONVEYOR, AN ELEVATOR MOVABLE BETWEEN THE DISCHARGE END OF SAID COLLECTION CONVEYOR WHEREAT IT RECEIVES THE DISCHARGE THEREFROM AND A REMOTE LOCATION FOR TRANSFERRING THERETO EACH DISCHARGE FROM SAID COLLECTION CONVEYOR, A SEPARATOR MECHANISM MOVABLE INTO SAID COLLECTION CONVEYOR FROM A POSITION LATERALLY OUTWARDLY THEREFROM AND ALSO BEING AXIALLY MOVABLE THERETHROUGH SO AS TO BE INSERTABLE INTO THE INTERFOLDED MATERIAL DISCHARGED FROM SAID INTERFOLDER TO DIVIDE THE MATERIAL INTO INDIVIDUAL STACKS OF WHICH THE MATERIAL DISPOSED BETWEEN SAID ELEVATOR AND ONE SIDE OF SAID SEPARATOR MECHANISM CONSTITUTES ONE SUCH STACK AND THE MATERIAL COLLECTING ALONG THE OPPOSITE SIDE OF SAID SEPARATOR CONSTITUTES ANOTHER STACK, AND DRIVE MECHANISM INCLUDING MEANS FOR SYNCHRONOUSLY ROTATING SAID CONVEYOR ELEMENTS ALSO INCLUDING MEANS FOR RECIPROCATING SAID ELEVATOR IN TIMED RELATION THEREWITH AND FURTHER INCLUDING MEANS FOR CYCLICALLY MOVING SAID SEPARATOR MECHANISM INTO AND OUT OF THE PATH OF SUCH INTERFOLDED MATERIAL AND AXIALLY THROUGH SAID COLLECTION CONVEYOR IN TIMED RELATION WITH THE ROTATIONAL MOVEMENT OF SAID CONVEYOR ELEMENTS TO EFFECT SUCH SEPARATION OF THE INTERFOLDED MATERIAL INTO STACKS. 